EP0347978A1 - Vérin pneumatique avec fermeture de la valve de commande par aimant permanent - Google Patents
Vérin pneumatique avec fermeture de la valve de commande par aimant permanent Download PDFInfo
- Publication number
- EP0347978A1 EP0347978A1 EP19890201535 EP89201535A EP0347978A1 EP 0347978 A1 EP0347978 A1 EP 0347978A1 EP 19890201535 EP19890201535 EP 19890201535 EP 89201535 A EP89201535 A EP 89201535A EP 0347978 A1 EP0347978 A1 EP 0347978A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- piston
- air
- valve
- source
- valve actuator
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 238000013016 damping Methods 0.000 claims abstract description 31
- 239000012530 fluid Substances 0.000 claims description 10
- 235000014676 Phragmites communis Nutrition 0.000 claims description 8
- 238000013459 approach Methods 0.000 claims description 8
- 230000000694 effects Effects 0.000 claims description 3
- 238000013022 venting Methods 0.000 claims description 2
- 230000003472 neutralizing effect Effects 0.000 claims 1
- 230000007246 mechanism Effects 0.000 abstract description 6
- 238000002485 combustion reaction Methods 0.000 abstract description 5
- 239000000543 intermediate Substances 0.000 description 12
- 238000004891 communication Methods 0.000 description 5
- 230000006854 communication Effects 0.000 description 5
- 230000002829 reductive effect Effects 0.000 description 5
- 230000000740 bleeding effect Effects 0.000 description 3
- 230000006872 improvement Effects 0.000 description 3
- 230000007704 transition Effects 0.000 description 3
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 2
- 230000003111 delayed effect Effects 0.000 description 2
- 239000007789 gas Substances 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 238000005381 potential energy Methods 0.000 description 2
- 230000001133 acceleration Effects 0.000 description 1
- 230000009471 action Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 238000004146 energy storage Methods 0.000 description 1
- 229910052742 iron Inorganic materials 0.000 description 1
- 230000000670 limiting effect Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000036961 partial effect Effects 0.000 description 1
- 238000011084 recovery Methods 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- 230000000284 resting effect Effects 0.000 description 1
- 230000001360 synchronised effect Effects 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
- F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
- F01L9/16—Pneumatic means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15C—FLUID-CIRCUIT ELEMENTS PREDOMINANTLY USED FOR COMPUTING OR CONTROL PURPOSES
- F15C1/00—Circuit elements having no moving parts
- F15C1/02—Details, e.g. special constructional devices for circuits with fluid elements, such as resistances, capacitive circuit elements; devices preventing reaction coupling in composite elements ; Switch boards; Programme devices
- F15C1/04—Means for controlling fluid streams to fluid devices, e.g. by electric signals or other signals, no mixing taking place between the signal and the flow to be controlled
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
- F01L9/20—Valve-gear or valve arrangements actuated non-mechanically by electric means
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/8593—Systems
- Y10T137/86493—Multi-way valve unit
- Y10T137/86574—Supply and exhaust
- Y10T137/86582—Pilot-actuated
- Y10T137/86614—Electric
Definitions
- the present invention relates generally to a two position, straight line motion actuator and more partucularly to a fast acting actuator which utilizes pneumatic energy against a piston to perform fast transit times between the two positions.
- the invention utilizes a pair of control valves to gate high pressure air to the piston and latching magnets to hold the valves in their closed positions until a timed short term electrical energy pulse excites a coil around a magnet to partially neutralize the magnet's holding force and release the associated valve to move in response to high pressure air from a pressure source to an open position.
- Stored pneumatic gases accelerate the piston rapidly from one position to the other position.
- intermediate pressure air fills a chamber applying an opposing force on the piston to slow the piston.
- a relief valve arrangement releases part of this trapped air back to the source.
- This actuator finds particular utility in opening and closing the gas exchange, i.e., intake or exhaust, valves of an otherwise conventional internal combustion engine. Due to its fast acting trait, the valves may be moved between full open and full closed positions almost immediately rather than gradually as is characteristic of cam actuated valves.
- the actuator mechanism may find numerous other applications such as in compressor valving and valving in other hydraulic or pneumatic devices, or as a fast acting control valve for fluidic actuators or mechanical actuators where fast controlled action is required such as moving items in a production line environment.
- the power or working piston which moves the engine valve between open and closed positions is separated from the latching components and certain control valving structures so that the mass to be moved is materially reduced allowing very rapid operation. Latching and release forces are also reduced. Those valving components which have been separated from the main piston need not travel the full length of the piston stroke, leading to some improvement in efficiency.
- a bistable fluid powered actuating device characterized by fast transition times and improved efficiency
- a pneumatically driven actuating device which is tolerant of variations in air pressure and other operating parameters
- an electronically controlled pneumatically powered valve actuating device having improved damping features
- the provision of a valve actuating device where a modest sacrifice in operating speed yields a significant increase in efficiency
- improvements in a pneumatically powered valve actuator where the control valves within the actuator cooperate with, but operate separately from the main working piston.
- a bistable electronically controlled fluid powered transducer has an armature including an air powered piston which is reciprocable along an axis between first and second positions along with a control valve reciprocable along the same axis between open and closed positions.
- a magnetic latching arrangement functions to hold the control valve in the closed position while an electromagnetic arrangement may be energized to temporarily neutralize the effect of the permanent magnet latching arrangement to release the control valve to move from the closed position to the open position.
- Energization of the electromagnetic arrangement causes movement of the valve in one direction along the axis first forming a sealed chamber including a portion of the armature and thereafter allowing fluid from a high pressure source to enter the closed chamber and drive the armature in the opposite direction from the first position to the second position along the axis.
- the distance between the first and second positions of the armature is typically greater than the distance between the open and closed positions of the valve.
- a pneumatically powered valve actuator includes a valve actuator housing with a piston reciprocable inside the housing along an axis.
- the piston has a pair of oppositely facing primary working surfaces.
- a pair of air control valves are reciprocable along the same axis relative to both the housing and the piston between open and closed positions.
- a coil is electrically energized to selectively opening one of the air control valves to supply pressurized air to one of the primary working surfaces causing the piston to move.
- Each of the air control valves includes an air pressure responsive surface which urges the control valve, when closed, against a spring bias toward its open position and there may be an air vent located about midway between the extreme positions of piston reciprocation for dumping expanded air from the one primary working surface and removing the accelerating force from the piston.
- the air vent also functions to introduce air at an intermediate pressure to be captured and compressed by the opposite primary working surface of the piston to slow piston motion as it nears one of the extreme positions.
- a one-way pressure relief valving arrangement such as a reed valve or check valve vents the captured air back to a high pressure air source.
- the air vent supplies intermediate pressure air to one primary working surface of the piston to temporarily hold the piston in one of its extreme positions pending the next opening of an air control valve.
- the air control valve is uniquely effective to vent air from the piston for a short time interval and at essentially source pressure back to the source and to finally dump air at a pressure not greater than source pressure after damping near the end of a piston stroke.
- the valve actuator is illustrated sequentially in Figures 1-9 to illustrate various component locations and functions in moving a poppet valve or other component (not shown) from a closed to an open position. Motion in the opposite direction will be clearly understood from the symmetry of the components.
- the actuator includes a shaft or stem 11 which may form a part of or connect to an internal combustion engine poppet valve.
- the acuator also includes a low mass reciprocable piston 13, and a pair of reciprocating or sliding control valve members 15 and 17 enclosed within a housing 19.
- the control valve members 15 and 17 are latched in one position by permanent magnets 21 and 23 and may be dislodged from their respective latched positions by energization of coils 25 and 27.
- the control valve members or shuttle valves 15 and 17 cooperate with both the piston 13 and the housing 19 to achieve the various porting functions during operation.
- the housing 19 has a high pressure inlet port 39, a low pressure outlet port 41 and an intermediate pressure port 43.
- the low pressure may be about atmospheric pressure while the intermediate pressure is about 10 psi. above atmospheric pressure and the high pressure is on the order of 100 psi. gauge pressure.
- Figure 1 shows an initial state with piston 13 in the extreme leftward position and with the air control valve 15 latched closed.
- the annular abutment end surface 29 is inserted into an annular slot in the housing 19 and seals against an o-ring 31. This seals the pressure in cavity 33 and prevents the application of any moving force to the main piston 13.
- the main position 13 is being urged to the left (latched) by the pressure in cavity or chamber 35 which is greater than the pressure in chamber or cavity 37.
- annular opening 45 is in its final open position after having rapidly released compressed air from cavity 37 at the end of a previous leftward piston stroke.
- the shuttle valve 15 has moved toward the left, for example, 0.05 in. while piston 13 has not yet moved toward the right.
- the air valve 15 has opened because of an electrical pulse applied to coil 25 which has temporarily neutralized the holding force on iron armature or plate 47 by permanent magnet 21.
- air pressure in cavity 33 which is applied to the air pressure responsive annular face 49 of valve 15 causes the valve to open.
- the communication between cavity 51 and the low pressure outlet port 41 has not been interrupted by movement of the valve 15. This communication is maintained at all times by way of a series of openings such as 54 in control valve 15.
- the edge of air valve 15 has overlapped the piston 13 at 53 closing annular opening 45 of Figure 1 creating a closed chamber to assure rapid pressurization and maximum acceleration of the piston 13.
- Figure 3 shows the opening of the air valve 15 to about 0.10 in. (2/3 of its total travel) and movement of the piston 13 about 0.025 in. to the right.
- the compression of wave washer 16 also stores potential energy to power the return of the control valve 15 to the closed position.
- the annular surface 62 which is shown as a portion of a right circular cylinder may be undercut (concave) or tapered (a conical surface) to restrict air flow more near one or both extremes of the travel of plate 47 to enhance damping without restricting motion intermediate the ends if desired.
- the piston 13 is continuing to accelerate toward the right in Figure 4 and the air valve 15 has nearly reached its maximum leftward open displacement.
- the valve will tend to remain in this position for a short time due to the continuing air pressure on the annular surface 49 from high pressure source 39.
- the wave washer or spring 16 functions as a spring bias means to provide damping of air control valve motion as the air control valve approaches an open position and provides a restorative force to aid rapid return of the air control valve to a closed position.
- the air valve 15 is still in its extreme leftward position.
- the air valve is designed to close at about the same time as the main piston arrives at its furthest right hand location. Also, in Figure 5, the piston is continuing to compress the air in cavity 35 slowing its motion.
- the reed valves 101 and 103 function to recapture part of the kinetic energy of the piston 13 when damping the piston motion by returning high pressure air to the source 33 rather than merely compressing air in the piston motion damping chamber 35 and then dumping that air to the atmosphere or to the intermediate pressure source.
- This annular opening vents the high pressure air from chamber 35 just as the piston nears its right hand resting position to help prevent any rebound of the piston back toward the left.
- the damping of the piston motion near its right extremity is adjustable by controlling the intermediate pressure level at port 43 to effectively control the density of the air initially entrapped in chamber 35. If this intermediate pressure is too high, the piston will rebound due to the high pressure of the compressed air in chamber 35. If this pressure is too low, the piston will approach its end position too fast and may mechanically rebound due to metallic deflection or mechanical spring back. With the correct pressure, the piston will gently come to rest in its right hand position.
- a further final damping of piston motion may be provided during the last few thousandths of an inch of travel by a small hydraulic damper including a fluid medium filled cavity 73 and a small piston 75 fastened to and moving with the main piston 13.
- the small piston 75 enters a shallow annular restricted area 77 displacing the fluid therefrom and bringing the main piston to rest.
- Fluid such as oil, may be supplied to the damping cavity 73 by way of inlet 85.
- valve 15 is about midway along its return to its closed position. Final damping is almost complete as the pressure in chamber 35 is being relieved through the annular opening at 69 and through the opening 81 and channel 83 to the low pressure port 41 so that the pressure throughout chamber 35 is reduced to nearly atmospheric pressure.
- valves 15 and 17 include a number of apertures such as 54 and 81 in their respective web portions allowing free air flow between chambers such as 35 and 83.
- the piston 13 is reaching a very low velocity, the damping is almost complete and the final damping by the small fluid piston 75 is underway.
- the main piston 13 has reached its righthand extreme in Figure 9 and air valve 15 has closed.
- the supply of high pressure air from the source 39 to chamber 37 and the surface 38 of piston 13 has long since been interrupted by piston edge 105 passing housing edge 55.
- the piston 13 is held or latched in the position shown by the intermediate pressure in chamber 37 from source 43 acting on piston face 38.
- a differentially controllable valving arrangement for controlling the thrust on the piston 13 including adjustable set screw 109 having a conical end surface 111 variably spaced from a similarly shaped seat 113 for supplying air from the pressurized source to the air control valves to compensate for variations in external forces opposing piston motion.
- Set screw 109 may be adjusted to vary the restriction between chamber 33 and channel 115 leading to control valve 15.
- the corresponding channel 117 leading to control valve 17 has a fixed restriction. The restriction tends to be self adjusting in the sense that if piston motion is opposed then the pressure driving the piston increases tending to correct for the increased opposition.
- Figures 10 and 11 are similar to Figure 1, but each illustrates a scheme wherein the pneumatic damping means is differentially adjustable to vary piston deceleration as the piston approaches one extremity relative to piston deceleration as the piston approaches the other extremity.
- the pneumatic damping means includes a volume varying adjustable member in Figure 10, and, in Figure 11, an adjustable member for controlling air wscape from the pneumatic damping means.
- a pair of adjustable set screws 119 and 121 seal corresponding holes leading to the chambers 36 and 35 respectively. Axial movement of one of these screws varies the volume of the piston motion damping chamber. When the piston is near the end of its travel, this small volume becomes a significant part of the total volume of the damping chamber and a change in that volume has a significant effect on the chamber pressure and, therefore, on the damping force. For example, if set screw 121 is withdrawn increasing the volume of chamber 35, the opening of reed valve 101 (at peak or source pressure) will be delayed until the piston is closer to its rightmost position. A fine tuning of the damping motion at one extreme of piston travel relative to damping at the other extreme is therefore possible.
- Such a fine tuning may also be achieved by bleeding air from the damping chamber as in Figure 11 rather than varying the volume of that chamber as in Figure 10.
- a pair of needle valves 123 and 125 control air seepage from the damping chambers, thereby controlling the time at which peak pressure occurs.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Theoretical Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Valve Device For Special Equipments (AREA)
- Magnetically Actuated Valves (AREA)
- Fluid-Driven Valves (AREA)
- Actuator (AREA)
- Fluid-Pressure Circuits (AREA)
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US209279 | 1988-06-20 | ||
US07/209,279 US4852528A (en) | 1988-06-20 | 1988-06-20 | Pneumatic actuator with permanent magnet control valve latching |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0347978A1 true EP0347978A1 (fr) | 1989-12-27 |
EP0347978B1 EP0347978B1 (fr) | 1993-12-08 |
Family
ID=22778127
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP19890201535 Expired - Lifetime EP0347978B1 (fr) | 1988-06-20 | 1989-06-14 | Vérin pneumatique avec fermeture de la valve de commande par aimant permanent |
Country Status (6)
Country | Link |
---|---|
US (1) | US4852528A (fr) |
EP (1) | EP0347978B1 (fr) |
JP (1) | JPH0240086A (fr) |
KR (1) | KR900000605A (fr) |
CA (1) | CA1324932C (fr) |
DE (1) | DE68911214T2 (fr) |
Families Citing this family (25)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2641336B1 (fr) * | 1988-12-30 | 1994-05-20 | Institut Francais Petrole | Dispositif et methode pour introduire un melange carbure dans une chambre d'un moteur a deux temps |
US4915015A (en) * | 1989-01-06 | 1990-04-10 | Magnavox Government And Industrial Electronics Company | Pneumatic actuator |
US4875441A (en) * | 1989-01-06 | 1989-10-24 | Magnavox Government And Industrial Electronics Company | Enhanced efficiency valve actuator |
US5003938A (en) * | 1989-12-26 | 1991-04-02 | Magnavox Government And Industrial Electronics Company | Pneumatically powered valve actuator |
US4974495A (en) * | 1989-12-26 | 1990-12-04 | Magnavox Government And Industrial Electronics Company | Electro-hydraulic valve actuator |
US5022359A (en) * | 1990-07-24 | 1991-06-11 | North American Philips Corporation | Actuator with energy recovery return |
US5109812A (en) * | 1991-04-04 | 1992-05-05 | North American Philips Corporation | Pneumatic preloaded actuator |
US5647318A (en) * | 1994-07-29 | 1997-07-15 | Caterpillar Inc. | Engine compression braking apparatus and method |
US5540201A (en) * | 1994-07-29 | 1996-07-30 | Caterpillar Inc. | Engine compression braking apparatus and method |
US5526784A (en) * | 1994-08-04 | 1996-06-18 | Caterpillar Inc. | Simultaneous exhaust valve opening braking system |
US6092545A (en) * | 1998-09-10 | 2000-07-25 | Hamilton Sundstrand Corporation | Magnetic actuated valve |
EP1329631A3 (fr) * | 2002-01-22 | 2003-10-22 | Jenbacher Zündsysteme GmbH | Moteur à combustion |
US8747084B2 (en) | 2010-07-21 | 2014-06-10 | Aperia Technologies, Inc. | Peristaltic pump |
WO2013066404A1 (fr) * | 2011-05-10 | 2013-05-10 | Aperia Technologies | Mécanisme de commande pour un système sous pression |
EP2828103B1 (fr) | 2012-03-20 | 2017-02-22 | Aperia Technologies | Système de gonflage de pneu |
EP2662139A1 (fr) | 2012-05-08 | 2013-11-13 | Roche Diagniostics GmbH | Soupape de distribution d'un fluide |
CN104919233B (zh) | 2013-01-14 | 2018-04-10 | 戴科知识产权控股有限责任公司 | 控制阀的活塞致动器以及操作该活塞致动器的方法 |
US10245908B2 (en) | 2016-09-06 | 2019-04-02 | Aperia Technologies, Inc. | System for tire inflation |
US9604157B2 (en) | 2013-03-12 | 2017-03-28 | Aperia Technologies, Inc. | Pump with water management |
US11453258B2 (en) | 2013-03-12 | 2022-09-27 | Aperia Technologies, Inc. | System for tire inflation |
US10144254B2 (en) | 2013-03-12 | 2018-12-04 | Aperia Technologies, Inc. | Tire inflation system |
SE540409C2 (sv) * | 2013-10-16 | 2018-09-11 | Freevalve Ab | Förbränningsmotor samt kåpsammansättning därför |
US10406869B2 (en) | 2017-11-10 | 2019-09-10 | Aperia Technologies, Inc. | Inflation system |
US10495233B2 (en) | 2017-12-21 | 2019-12-03 | Honeywell International Inc. | Three-position valve and pneumatic actuator therefor |
US11642920B2 (en) | 2018-11-27 | 2023-05-09 | Aperia Technologies, Inc. | Hub-integrated inflation system |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE421002C (de) * | 1925-11-04 | D Aviat Louis Breguet Sa Des A | Steuerung von Ventilen, insbesondere fuer Explosionsmotoren, durch Fluessigkeiten oder Gase | |
US3844528A (en) * | 1971-12-30 | 1974-10-29 | P Massie | Electrically operated hydraulic valve particularly adapted for pollution-free electronically controlled internal combustion engine |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE197808C (fr) * | ||||
US2552960A (en) * | 1946-09-27 | 1951-05-15 | Nordberg Manufacturing Co | Gas actuated inlet valve |
CH592835A5 (fr) * | 1975-04-29 | 1977-11-15 | Lucifer Sa | |
CH620748A5 (fr) * | 1978-04-04 | 1980-12-15 | Lucifer Sa | |
DE3500530A1 (de) * | 1985-01-09 | 1986-07-10 | Binder Magnete GmbH, 7730 Villingen-Schwenningen | Vorrichtung zur elektromagnetischen steuerung von hubventilen |
US4605197A (en) * | 1985-01-18 | 1986-08-12 | Fema Corporation | Proportional and latching pressure control device |
-
1988
- 1988-06-20 US US07/209,279 patent/US4852528A/en not_active Expired - Fee Related
-
1989
- 1989-06-14 DE DE68911214T patent/DE68911214T2/de not_active Expired - Fee Related
- 1989-06-14 EP EP19890201535 patent/EP0347978B1/fr not_active Expired - Lifetime
- 1989-06-16 CA CA 603002 patent/CA1324932C/fr not_active Expired - Fee Related
- 1989-06-16 KR KR1019890008295A patent/KR900000605A/ko not_active Application Discontinuation
- 1989-06-20 JP JP1155919A patent/JPH0240086A/ja active Pending
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE421002C (de) * | 1925-11-04 | D Aviat Louis Breguet Sa Des A | Steuerung von Ventilen, insbesondere fuer Explosionsmotoren, durch Fluessigkeiten oder Gase | |
US3844528A (en) * | 1971-12-30 | 1974-10-29 | P Massie | Electrically operated hydraulic valve particularly adapted for pollution-free electronically controlled internal combustion engine |
Also Published As
Publication number | Publication date |
---|---|
DE68911214T2 (de) | 1994-06-01 |
KR900000605A (ko) | 1990-01-30 |
DE68911214D1 (de) | 1994-01-20 |
US4852528A (en) | 1989-08-01 |
CA1324932C (fr) | 1993-12-07 |
JPH0240086A (ja) | 1990-02-08 |
EP0347978B1 (fr) | 1993-12-08 |
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